Infinitely Variable Multi-Epicyclic Friction Transmission System for Electric Motor

ABSTRACT

Infinitely variable multi-epicyclic friction transmission system including a main shaft, ball race discs, a splined tube, and twin planetary cone assemblies attached to a planetary carrier and disposed circumferentially around the splined tube. Each twin planetary cone assembly comprises a torque tube and a planetary cone-hemisphere structure comprising a planetary cone integral with hemisphere at its apex, wherein the planetary cone-hemisphere structure rolls inside the torque tube via the hemisphere, and wherein a slant height of the twin planetary cone assemblies is parallel to the main shaft. System also includes a series of spherical planets, a reaction ring disposed around the twin planetary cone assemblies configured to slide along the planetary cone assemblies to vary a gear ratio, and ball gear retaining rings. Each of the ball gear retaining rings is mounted on one of a plurality of ball gears which are mounted on the ball race discs.

This application is a continuation-in-part of U.S. patent applicationSer. No. 17/323,160, filed 18 May 2021, which is a continuation-in-partof U.S. patent application Ser. No. 16/560,041, filed 4 Sep. 2019,issued as U.S. Pat. No. 11,009,107, the specifications of which arehereby incorporated herein by reference.

BACKGROUND OF THE INVENTION Field of the Invention

At least one embodiment of the invention relates to electric motors, andin particular to an infinitely variable transmission system for electricmotors.

DESCRIPTION OF THE RELATED ART

An electric vehicle (EV), also referred to as an electric drive vehicle,uses one or more electric motors or traction motors for propulsion. Anelectric vehicle may be powered through a collector system byelectricity from off-vehicle sources, or may be self-contained with abattery or generator to convert fuel to electricity. EVs include roadand rail vehicles, surface and underwater vessels, electric aircraft andelectric spacecraft.

In the context of electric road vehicles, at present ‘range anxiety’ isnot a problem for city driving with a short commute to work and leisureactivities. However, ‘range anxiety’ occurs for long journeys over 100kilometres.

Continuously variable transmission (CVT), also known as a single-speedtransmission, stepless transmission, pulley transmission, or, in case ofmotorcycles, a twist-and-go, is an automatic transmission that canchange seamlessly through a continuous range of effective gear ratios.This contrasts with other mechanical transmissions that offer a fixednumber of gear ratios. The flexibility of a CVT allows the input shaftto maintain a constant angular velocity. A belt-driven design offersapproximately 88% efficiency, which, while lower than that of a manualtransmission, can be offset by lower production costs and by enablingthe engine to run at its most efficient speed for a range of outputspeeds. When power is more important than economy, the ratio of the CVTcan be changed to allow the engine to turn at the RPM at which itproduces greatest power. This is typically higher than the RPM thatachieves peak efficiency. In low-mass low-torque applications abelt-driven CVT also offers ease of use and mechanical simplicity. Steelbelt-driven CVTs are now the dominant variable transmission used incars.

Epicyclic gearing or planetary gearing is a gear system comprising oneor more outer gears, or planet gears, revolving about a naseral, or sungear. Typically, naser gears are mounted on a movable arm or carrierwhich itself may rotate relative to the sun gear. Epicyclic gearingsystems also comprise an outer ring gear or annulus, which meshes withthe planet gears. Planetary gears, or epicyclic gears, are typicallyclassified as simple or compound planetary gears. Simple planetary gearshave one sun, one ring, one carrier, and one planet set. Compoundplanetary gears may comprise one or more of the following three types ofstructures: meshed-planet—there are at least two more planets in meshwith each other in each planet train, stepped-planet—there exists ashaft connection between two planets in each planet train, andmulti-stage structures—the system contains two or more planet sets.Compared to simple planetary gears, compound planetary gears have theadvantages of larger reduction ratio, higher torque-to-weight ratio, andmore flexible configurations.

Epicyclic gearing with toothed gear wheels is very common in automaticgear boxes. A friction drive or friction engine is a type oftransmission that, instead of a chain and sprockets, uses two wheels inthe transmission to transfer power to the driving wheels.

The problem with this type of drive system is that it is not veryefficient. Trying to duplicate epicyclic gearing with friction drives isvery difficult because if the planets are mounted on fixed stubs and atfixed distances from each other, they cannot be forced against othercomponents to give a friction drive.

A cone CVT varies the effective gear ratio using one or more conicalrollers. The simplest type of cone CVT, a single-cone CVT, uses a wheelthat moves along the slope of the cone, creating the variation betweenthe narrow and wide diameters of the cone. In a planetary CVT, the gearratio is shifted by tilting the axes of spheres in a continuous fashion,to provide different contact radii, which in turn drive input and outputdiscs. The system can have multiple planets to transfer torque throughmultiple fluid patches.

In view of the above, there is a need to provide an improvedtransmission system for electric motors, as it is no longer a questionof whether electric vehicles will form a significant part oftransportation. The quest now is to get a greater range with a givencharge. Undoubtedly, battery technology will be the key here withnanotechnology playing a major role. An infinitely variable gearboxwould also help but would have to be very efficient to make asignificant contribution.

BRIEF SUMMARY OF THE INVENTION

The present disclosure provides a mechanism for increasing the torquecapacity of an infinitely variable transmission system which reliessolely on rolling friction. This is accomplished by having a stack ofepicyclic friction gears in series.

The transmission system of the present disclosure may be configured tohave sufficient torque at its output to drive the road wheels of a motorvehicle. The greatly enhanced output of torque that the system producesis by means of its multi-epicyclics stacked in series. These work in ananalogous way to a multi-plate clutch where friction discs arecompressed in series to transmit much more torque by static frictionthan by one pair of discs alone.

In a further aspect of the disclosure, there is provided an infinitelyvariable multi-epicyclic friction transmission system for an electricmotor, the system comprising:

-   -   a main shaft;    -   a cylindrical drum which can be stepped down to a narrower        diameter at one end and which is disposed axially around the        main shaft; the drum configured to bear a series of inverted        vee-rings or the like, and splined on an outer circumferential        surface so that the rings can slide longitudinally along the        cylindrical drum;    -   an axial flux motor comprising a stator which is fixedly located        in one of the casings side plates;    -   a default thrust bearing mounted on the main shaft between the        rotor and the stator to prevent physical contact therebetween;    -   a plurality of twin planetary cone assemblies attached to the at        least one planetary carrier and disposed circumferentially        around the cylindrical drum each twin planetary cone assembly        comprising: a torque tube and a planetary cone-hemisphere        structure provided at each end of the torque tube, wherein each        planetary cone-hemisphere structure comprises a planetary cone        integral with a hemisphere at its apex, wherein each planetary        cone-hemisphere structure is configured to roll inside a        respective torque tube via a respective hemisphere, and wherein        the slant height of each planetary cone is parallel to the main        shaft;    -   a series of spherical planets configured to alternate with the        series of inverted vee-rings,    -   wherein the vee-rings are configured to be compressed together        by a pressuriser ring at a distal end of the cylindrical drum,        thus forcing the spherical planets radially outwards to abut the        torque tubes; and further comprising:    -   at least one reaction ring disposed around each of the twin        planetary cone assemblies and configured to slide along a        planetary cone of each twin planetary cone assembly to vary a        gear ratio;    -   a pressure plate between each planetary carrier and the base of        the planetary cones such that pressure plates force the        planetary cones inwards into the torque tubes providing        frictional adhesion between the hemispheres and the torque tubes        internally and the cones and torque tubes externally; and    -   a plurality of idler planets mounted on a plurality of rods        connecting planetary carrier halves.

The function of the axial flux motor is not only to rotate the planetcarrier but to utilise its powerful magnetic force to attract the rotorand instantly compress the system when electric power is turned on, thusaugmenting the pressurisation via the load.

In one or more embodiments, a circumference of each of the pressureplates has open ended slots such that a shaft of each twin planetarycone assembly can slide in them.

In one or more embodiments, the planetary cone and the torque tube aredimensioned such that their circles of contact are the same diameter onthe torque tube and the hemispheres.

In one or more embodiments, the number of idler planets is double thenumber of the torque tubes.

In one or more embodiments, the diameter of each idler planet is lessthan or equal to about half the diameter of each torque tube.

In one or more embodiments, the electric motor is located at an extremeend of the system.

In one or more embodiments, the vee-rings are configured to becompressed together from the distal end of the cylindrical drum towardsthe motor end of the cylindrical drum thus forcing the spherical planetsradially outwards.

In one or more embodiments, the rotor comprises a disc with magnets, ina halbach array or otherwise, bonded onto the surface facing the statorand mounted on the main shaft.

In one or more embodiments, each of the pressuriser rings is configuredto be engaged with a splined driver on the main shaft.

In one or more embodiments, the pressuriser ring comprises bearingsconfigured to roll on end rings disposed on the cylindrical drum,wherein, when the main shaft is rotated, the bearings roll on the endrings forcing the end rings to move longitudinally along the cylindricaldrum and compress the vee-rings, forcing the spherical planets radiallyoutwards.

In one or more embodiments, each planetary cone assembly is configuredto move out radially away from the main shaft.

In one or more embodiments, the plurality of twin planetary coneassemblies are mounted in the planetary carrier.

In one or more embodiments, the at least one planetary carrier comprisestwo planetary carriers coupled to each other and mounted on the mainshaft.

In one or more embodiments, the at least one reaction ring comprises tworeaction rings disposed around the plurality of planetary cones oneither side of the cylindrical drum and configured to slide along theplanetary cones to vary a gear ratio.

In one or more embodiments, the system comprises between three and sixtwin planetary cone assemblies.

BRIEF DESCRIPTION OF THE DRAWINGS

The present application will now be described with reference to theaccompanying drawings in which:

FIG. 1 illustrates an exploded view of some of the components of aninfinitely variable multi-epicyclic friction transmission systemaccording to an embodiment of the present disclosure;

FIGS. 2 and 2 a illustrate two different types of planetary carrier,according to embodiments of the present disclosure;

FIGS. 3 and 4 illustrate a structure in which a series of vee-rings andintermediate spherical gears are loaded about a main shaft of themechanism of FIG. 1, according to an embodiment of the presentdisclosure;

FIGS. 4A and 4B show a pressuriser ring and how it engages with an endring, according to an embodiment of the present disclosure;

FIG. 4C is a schematic of the forces involved when the transmission ispressurised;

FIGS. 5 and 5A illustrate two planetary cone-hemisphere arrangements,according to embodiments of the present disclosure;

FIG. 6 illustrates an end view of the transmission mechanism, accordingto an embodiment of the present disclosure;

FIG. 7 is a perspective view of how all the outer components of thetransmission system are configured and encased, according to anembodiment of the present disclosure;

FIG. 8 illustrates two views of a reaction ring according to anembodiment of the present disclosure;

FIG. 9 illustrates a multi-component view of an infinitely variabletransmission system according to an embodiment of the presentdisclosure;

FIG. 10 shows as many of the components as possible without obscuringothers;

FIG. 11A-D illustrates an exploded view of some of the components of aninfinitely variable multi-epicyclic friction transmission systemaccording to a second embodiment of the present disclosure;

FIGS. 12 and 12A illustrate two different types of planetary carrier,according to a second embodiment of the present disclosure;

FIGS. 13 and 14 illustrate a second embodiment of a structure in which aseries of vee-rings and intermediate spherical gears are loaded about amain shaft of the mechanism of FIGS. 11A-D, according to an embodimentof the present disclosure;

FIG. 14 shows a pressuriser ring and how it engages with an end ring,according to a second embodiment of the present disclosure;

FIG. 15 illustrate two planetary cone-hemisphere arrangements, accordingto a second embodiment of the present disclosure;

FIG. 16 illustrates an end view of the transmission mechanism, accordingto a second embodiment of the present disclosure;

FIG. 17 is a perspective view of how all the outer components of thetransmission system are configured and encased and two views of areaction ring according to a second embodiment of the presentdisclosure;

FIG. 18 and FIG. 19 illustrate multi-component views of an infinitelyvariable transmission system according to at least one embodiment of thepresent disclosure.

FIGS. 20A to 29 show an alternative embodiment in which there are noidler planets, and the two pressuriser rings are replaced by a singlepressuriser plate which is different in form and function to thatillustrated in the previous Figures.

FIG. 20A shows the main shaft and the thrust bearing which is betweenthe spider arms and the rotor tube.

FIG. 20B shows the splined tube to mount ball race discs.

FIG. 20C is the same as FIG. 11C but without the two pressurizer plates.

FIG. 20D shows the new pressurizer plate which replaces the twopressurizer rings, and which comprises three cutaways to accommodate thenarrow ends of the cones. FIG. 20D also shows thrust bearing which isbetween the new pressurizer plate and the end ball race disc.

FIG. 21 shows how two half planet carriers are combined together in adifferent way to the preceding embodiments.

FIG. 22 shows the rotor of the axial flux motor.

FIG. 23 is a perspective of ten ball race discs located around the mainshaft and splined tube.

FIG. 24 shows a drawing with the same ten ball race discs and theirassociated ball gears.

FIG. 25 is the same FIG. 15 but without the two pressurizing rings.

FIG. 26 shows a cross section of the transmission according to theembodiment of FIGS. 20A-29.

FIG. 27 is the same as FIG. 17 except that the stator of the electricmotor is in the right casing.

FIG. 28 shows the motor stator in the right casing and the default.

FIG. 29 shows as many components as possible without obscuring others.

DETAILED DESCRIPTION OF THE INVENTION

The present disclosure provides an infinitely variable transmissionsystem for an electric motor. The infinitely variable transmissionsystem according to the present disclosure comprises a planetary conetransmission system, but unlike most planetary transmissions it has notoothed gear wheels whatsoever. The transmission system according to thepresent disclosure can therefore be classified as a friction gearingsystem. The driving force is produced by rolling friction only. Frictiongearing is seldom used as it is incapable of transmitting much power.

The transmission system according to the present disclosure may be usedfor a range of electric motors.

Accordingly, the present disclosure provides an infinitely variablemulti-epicyclic friction transmission system for an electric motor, thesystem comprising: a main shaft; a motor drum comprising twocylindrically shaped half-drums disposed axially around the main shaftand separated by a longitudinal gap, the half-drums configured to bear aseries of inverted vee-rings splined on an outer circumferential surfaceof the half-drums so as to be configured to slide longitudinally alongthe half-drums; a rotor configured to be accommodated in a cavitydefined by the half-drums, the rotor comprising a rotor carrier driverconfigured to be disposed in the longitudinal gap for rotating at leastone planetary carrier about the main shaft; a plurality of twinplanetary cone assemblies attached to the at least one planetary carrierand disposed circumferentially around the two half-drums, each twinplanetary cone assembly comprising: a torque tube and a planetarycone-hemisphere structure provided at each end of the torque tube,wherein each planetary cone-hemisphere structure comprises a planetarycone integral with a hemisphere at its apex, wherein the planetarycone-hemisphere structure is configured to roll inside the torque tubevia the hemisphere, and wherein the slant height of the planetary conesis parallel to the main shaft; a series of spherical planets configuredto alternate with the series of inverted vee-rings, wherein thevee-rings are configured to be compressed together by a pressuriser ringat a distal end of each of the half-drums, thus forcing the sphericalplanets radially outwards to abut the torque tubes; and furthercomprising: at least one reaction ring disposed around the plurality ofplanetary cones and configured to slide along the planetary cones tovary a gear ratio.

The at least one reaction ring may comprises two reaction rings disposedaround the plurality of planetary cones on either side of the half-drumsand configured to slide along the planetary cones to vary the gearratio. The basic principle of the system is to force the twin planetarycone assemblies onto the reaction rings with as great a force aspossible. When multi-epicyclics are connected in series the originalforce is transmitted to the next member and so on. The at least oneplanetary carrier may comprise two planetary carriers coupled to eachother and mounted on the main shaft.

The system of the present disclosure may be configured to havesufficient power at its output to drive the road wheels of a motorvehicle. The greatly enhanced torque output that the system produces isby means of multi-epicyclics stacked in series. This is analogous to amultiplate clutch where friction discs are compressed in series totransmit much more torque by static friction than by one pair of discsalone.

In the system described herein where rolling friction is involved thereare a series of inverted vee-rings alternating with a series ofspherical planets therebetween. Each vee-ring and each spherical planettogether constitute a separate epicyclic gear train; the vee-ring beingthe sun gear, the spherical planet the inner planet and the torque tubetheir common outer planet. Hence the term multi-epicyclic usedthroughout the description. The vee-rings and the intermediate sphericalplanets are configured to be compressed and the spherical planets forcedout radially.

The system described has a plurality of twin planetary cone assemblies.Between three and six such assemblies may be employed. It has beendetermined through experimentation that six such assemblies is themaximum that can advantageously be used. Using six assembles may nottransmit more power but due to the very high forces involved the loadmay be distributed over a greater number of components. The twinplanetary cone assemblies may be mounted in at least one planetarycarrier. Each twin planetary cone assembly may comprise two largelyhollow planetary cones inside a torque tube. The two planetary cones,one at each end of the torque tube may be configured to transmit powerat a fixed angle unlike a constant velocity joint in a car where theangle can vary. The reason for the fixed angle is to keep the slantheight of the planetary cone parallel to the main axis. By keeping theslant height of the planetary cone parallel to the main axis, the one ormore reaction rings can slide easily along the cones to vary the gearratio.

The vee-rings and the intermediate spherical planets are configured tobe compressed and the spherical planets forced out radially. Suchcompression may be effected in a number of ways. FIGS. 1 and 2illustrate an example of a configuration for achieving such compression,according to an embodiment of the present disclosure.

FIG. 1 illustrates an exploded view of some of the components of aninfinitely variable multi-epicyclic friction transmission systemaccording to an embodiment of the present disclosure. More specifically,FIG. 1 illustrates a main shaft 1, a motor rotor 34, a motor drumcomprising two half-drums 3 for accommodating a motor, and twopressuriser rings 4, and how they are assembled together. The motor drumcomprising two half-drums 3 are disposed axially around the main shaft1. That is, the main shaft 1 extends longitudinally through a centre ofthe motor drum. The half-drums 3 extend longitudinally parallel to themain shaft 1. Slip rings 38 may be provided on the main shaft 1 to feedpower into the motor, as illustrated in FIG. 1. It can be seen in FIG. 1that there is ample space inside the half-drums 3 to accommodate anelectric motor, or specifically, the rotor 34. This is a major featureof the system in that space is saved by having the motor inside thetransmission. Referring to FIG. 1, the transmission is pressurized fromthe outer ends towards the centre. This will be explained later. In theembodiment illustrated in FIG. 1, a single electric motor may fit neatlyin the centre of the transmission. The motor drum constitutes the statorof the electric motor, and defines a cavity therethrough foraccommodating the rotor 34. The half-drums 3 may be splined to allowvee-rings 6 to slide longitudinally along an outer circumference of thehalf-drums 3. Open ends of the half-drums 3 are configured to face eachother. Magnets may be mounted on the inner circumference of eachhalf-drum 3. Each identical half-drum 3 comprises two concentriccylinders with an apertured disc welded onto a distal end thereof. Thetwo concentric cylinders comprise an inner cylinder and an outercylinder. The inner cylinder or more properly a tube is slightly longerthan the outer cylinder so that when the half-drums 3 are broughttogether a longitudinal gap is defined between the two outer cylinders.The longitudinal direction will be understood as being in the directionof the main shaft 1. The rotor comprises a rotor carrier driver 2configured to be disposed in the longitudinal gap for rotating at leastone planetary carrier about the main shaft 1. The rotor 34 does notdrive the main shaft 1 directly but indirectly through the infinitelyvariable transmission system. The rotor carrier driver 2 may compriseone or more rotor carrier driver stubs 2 mounted on the centre of therotor 34 which can rotate freely in the longitudinal gap. The one ormore rotor carrier driver stubs 2 may be configured to protrude radiallyfrom the centre of the rotor and configured to rotate in thelongitudinal gap. Referring to FIG. 1, the rotor carrier driver 2 maycomprise two diametrically opposite rotor carrier driver stubs 2 mountedon the centre of the rotor 34 which can rotate freely in thelongitudinal gap. In this manner, the rotor 3 can be rotated around themain shaft 1. Roller bearings 33 may be provided on the main shaft 1 toallow the rotor 34 to rotate about the main shaft 1. One or more rodsconnected to the at least one planetary carrier may be configured topass through the one or more rotor carrier driver stubs, thus allowingthe rotor to drive the planetary carrier. More specifically, rodsconnecting the at least one planetary carrier together pass throughapertures in the one or more rotor carrier driver stubs 2 and by thismeans the rotor 34 drives the at least one planetary carrier. The atleast one planetary carrier will be described later.

Referring to FIG. 1, flanges 3 a may be provided at the open ends of thehalf-drums 3 to keep the vee-rings 6 on the half-drums 3. FIG. 1 showsjust one vee-ring 6 on each half-drum 3. The more vee-rings the moretorque the transmission can handle. There is a limit to the number ofvee-rings that can be practically used. In one embodiment, fivevee-rings may be used on each half-drum 3; see FIG. 10. The vee-ringsmay be of triangular section as the term vee-rings suggest, but thevee-rings may also be of curved section. In this case the vee-rings mayresemble inner races of two ball thrust bearings, back to back. Theradius of curvature of the spherical planets may be only slightly lessthan the radius of curvature of the vee-rings. In a ball thrust bearing,the ball bearings are free to move outwards in their cages but they donot move to any appreciable extent before they are forced against theouter race. A very important point to note with this transmission isthat the spherical gears behave in a similar fashion. The sphericalgears are free to move out but do not to any appreciable extent becausein this case the space between the torque tubes prevents them from doingso.

FIG. 1 illustrates a pressuriser ring 4 at both ends of thetransmission, according to an embodiment of the present disclosure. Eachof the pressuriser rings 4 comprises an apertured disc having aplurality of outer arms 13. In the embodiment illustrated in FIG. 1, thepressuriser ring 4 comprises four outer arms 13. A roller bearing 5 maybe provided on each outer arm 13. The roller bearings 5 may beconfigured to engage with end rings 7 on each side of the transmission.The end rings 7 are illustrated in FIGS. 3 and 4 for example. Each ofthe pressuriser rings 4 may be configured to be engaged with a splineddriver on the main shaft 1. The two pressuriser rings 4 may be splinedon to the main shaft 1 and may be secured by nuts 14.

FIGS. 2 and 2 a illustrate two different types of planetary carrier 11,according to embodiments of the present disclosure. Each planetarycarrier 11 may have eight planetary cone shafts 26 fixedly attached toan apertured disc. In one embodiment, illustrated in FIG. 2, rods 12keep the planetary carriers 11 a fixed distance apart; in the other,illustrated in FIG. 2a , the planetary carriers 11 can move apart. Rotorpositioning nuts 9 may be provided on the rods 12 for positioning therotor 34.

FIG. 2 shows two planetary carriers 11 attached together with connectingrods 12. Only two connecting rods 12 are shown for clarity. The twodiametrically opposite connecting rods 12 may be threaded throughapertures 18 in the rotor carrier driver 2.

In FIG. 2a the planetary carriers 11 are similar in appearance to theplanetary carriers 11 of FIG. 2, but operate in a completely differentway and use a different type of planet. The arrangement of FIG. 2a alsoproves much greater adhesion between the contact surfaces. Whereas inFIG. 2, the planets are forced out radially by having them slide towardsthe centre, in FIG. 2a the planets are held longitudinally stationaryand the planetary carriers 11 pulled apart, thereby forcing the planetsout radially. This mechanism enables the torque tube to contact the conein two places and the cone to contact the reaction ring. The reallysignificant thing is that all these three contacts are pressurised inseries.

FIG. 2a represents an expandable planetary carrier 11. The planetarycarriers 11 of FIG. 2a which are of an expandable design may also bemounted on the main shaft 1 with the same bearings but are not boltedtogether. The arrangement of FIG. 2a is a modification of the embodimentof FIG. 2 which has eight connecting rods 12 each of which has both endsfixedly attached to its planetary carrier 11. The arrangement of FIG. 2ahas four connecting rods 12 fixedly attached to one of the planetarycarriers 11. The other ends of the connecting rods 12 are free to slidein apertures 18 in the other planetary carrier 11. The apertures 18 inthe planetary carriers 11 may be provided with a greased bush bearing.The free ends of the connecting rods 12 may have springs anchored attheir ends to assist in pushing the planetary carriers 11 apart andprovide initial adhesion. The planetary carriers 11 of FIG. 2a althoughof a more complicated design allows for a superior pressurizingmechanism which will be explained in later figures.

FIG. 3 is a perspective view illustrating a series of the vee-rings 6arranged about the main shaft 1, according to an embodiment of thepresent disclosure. The series of vee-rings 6 comprises two banks ofvee-rings 6 on either side of the main shaft 1. In the embodimentillustrated in FIG. 3, the series of vee-rings 6 comprises fourvee-rings 6 on either side of the main shaft 1. As illustrated in FIG.4, the rotor 34 is positioned between the two banks of four vee-rings 6on either side. It will be understood that the vee-rings 6 are providedon an outer circumferential surface of the half-drums 3, wherein thevee-rings 6 are configured to slide along the half-drums 3. Fourvee-rings 6 may be bounded on one side by an end ring 8 with an inclineon one side only. On the other side is an end ring 7 with an incline onone side only but with cam inclines on the other side.

FIG. 4 is a cross-sectional view of the structure of FIG. 3 according toan embodiment of the present disclosure. Referring to FIG. 4, sphericalplanets 19 are illustrated. The spherical planets 19 may be consideredto be frictional ball gears. The spherical planets 19 are in a realsense gears and can be considered to be the inner planets of anepicyclic gear set.

The circumference of the v-rings 6 may be of triangular section orcurved section as illustrated in FIG. 4. With the curved section thev-rings 6 may be exactly the same as the inner races of the sphericalplanets 19. The individual vee-rings 6 in FIG. 4 are like two such innerraces welded together back to back. The circular curves of the vee-rings6 may have a slightly greater radius than the radius of the sphericalplanets 19. Unlike a ball bearing a cage is not required as the torquetubes space the bearings. In FIG. 4, compression of the end rings 7forces the spherical planets 19 into the space between the torque tubes,as illustrated in FIG. 4C and FIG. 9.

FIGS. 4A and 4B illustrate the pressuriser rings 4 and how they engagewith the end rings 7 on the main shaft 1, according to an embodiment ofthe present disclosure. The pressuriser rings 4 are configured to besplined onto the main shaft 1. FIG. 4A is an end view of the pressuriserring 4 with four roller bearings 5 on each outer arm 13. FIG. 4B showshow the roller bearings 5 fit into the cams of the end ring 7. FIG. 4Cis a schematic drawing of how the pressuriser ring 4 works and how aforce of one unit generates a radial force of twenty units. That is, thepressuriser rings 4 function to compress the vee-rings 6 and theintermediate spherical planets 19 together and force the sphericalplanets 19 out radially. The greater the load the transmissionencounters, the greater the force. Referring to FIG. 4C, each planetarycone assembly comprises a torque tube 17 constituting a common outerplanet attached to a planetary cone 22 at each end thereof. The slantheight of the planetary cone 22 is parallel to the main shaft 1. Areaction ring 25 is disposed around each planetary cone 22 andconfigured to slide along the planetary cone 22 to vary a gear ratio.

Referring to FIGS. 1 and 4C, the pressuriser ring 4 with roller bearings5 may be configured to be slid onto the main shaft 1 and engage with theend rings 7. If the main shaft 1 is rotated in one direction and then inthe other direction the pressuriser ring 4 will move several degreeseach way. The roller bearings 5 of the pressuriser ring 4 roll on theend rings 7 forcing the end rings 7 out sideways or in a longitudinalaxis direction. Thus, when the main shaft 1 is rotated, the bearings 5of the pressuriser ring 4 roll on the inclines of the end rings 7forcing the end rings 7 to move longitudinally along the half-drums 3and compress the vee-rings 6, forcing the spherical planets 19 radiallyoutwards.

FIGS. 5 and 5A illustrate twin planetary cone assemblies according toembodiments of the present disclosure. Each twin planetary cone assemblycomprises two planetary cone-hemisphere structures at either end of atorque tube 17. FIG. 5 illustrates two planetary cone-hemispherestructures. Referring to FIG. 5, each planetary cone-hemispherestructure 22 comprises a planetary cone 22 integral with a hemisphere 27at its apex. Each planetary cone-hemisphere structure may be mounted ona planetary cone shaft 26. The planetary cone shafts 26 may be attachedto the planetary carriers 11 at such an angle that the slant height ofthe mounted planetary cones 22 is parallel to the main axis 1.

Each twin planetary cone assembly also comprises a torque tube 17. Thetorque tube 17 may be cylindrically shaped. The planetarycone-hemisphere structures may be provided at ends of the torque tube17. The hemispheres 27 may be configured to be a sliding fit inside thetorque tube 17. The torque tube 17 may comprise a plurality of fixedrings 43 on inner surfaces thereof and integral with the torque tube 17.The fixed rings 43 may be configured to prevent excessive longitudinalfloat of the torque tube 17.

A small space may be left between the ends of the hemispheres 27 and theends of the planetary cone shafts 26 so that the planetary cones 22 canmove out radially and consequently the torque tubes 17. Thisarrangement—a shaft inside a hollow tube—enables the torque tube 17 tomove out radially, while the planetary cone shaft 26 being fixed in theplanetary carrier 11 cannot and remains at a fixed radial distance. Itis the potential to move out radially that is important. The torque tube17 and the spherical planets 19 may be configured to move out radiallycausing the torque tubes 17 to diverge from each other and the sphericalplanets 19 to escape. The spherical planets 19 may be configured to abutthe reaction rings 25 so that the torque tubes 17 cannot move outradially. However, the spherical planets 19 can be pressurized and thisdisclosure shows how great the pressure between components can be.Referring to the embodiment of FIG. 2A, as well as the planetarycarriers 11 being free to move laterally apart, the planetarycone-hemisphere structures may be configured to slide on the planetarycone shafts 26. Once the planetary cones 22 abut the reaction rings 25all these movements stop.

The embodiment of FIG. 5A uses the planetary carrier 11 of FIG. 2a and adifferent planetary cone-hemisphere structure according to anotherembodiment of the present disclosure. The planetary cone-hemispherestructure of FIG. 5 comprises a hemisphere 27 attached to a planetarycone 22, wherein the hemisphere 27 is a sliding fit inside the torquetube 17. In FIG. 5A the hemisphere 27 a of the planetary cone-hemispherestructure has an outer diameter significantly less than the internaldiameter of the torque tube 17. In addition, the hemisphere 27 a of FIG.5A is configured such as to have a conical surface facing the planetarycone 22 a itself. There is line contact by pure rolling friction betweenthis conical surface and conical rings 43 a inside the torque tube 17.The conical rings 43 a perform a completely different function to thefixed rings 43 in FIG. 5 which keeps the torque tube 17 in place and issubjected to no great pressure. The conical rings 43 a are configured toprevent the planetary cones 22 a being pulled out of the torque tube 17under great force.

The ends of the torque tube 17 are forced out against the planetarycones 22 a. The circle of contact, represented by dotted lines in FIG.5A, may be of equal diameter to the circle of contact the planetarycone-hemisphere structure makes with the torque tube 17. The set-upposition is as in FIG. 5A with the relevant surfaces in contact.

If initially there are gaps between the planetary cone-hemispherestructure and the conical rings 43 a and between the planetary cones 22a and the reaction rings 25 one can examine what happens when the systemis pressurized. The result of the outward radial force of the torquetube 17 on the planetary cones 22 a may be to force the planetary cones22 a sideways and bring the planetary cone-hemisphere structure againstthe conical ring 43 a. When the planetary cones 22 a can go no longersideways the component of the force acting on the planetary cone shaft26 may force the planetary carrier 11 sideways forcing the planetarycones 22 a against the reaction rings 25. The planetary cones 22 a maybe mounted on caged roller bearings 50 which are configured to slidealong the planetary cone shafts 26. Having loaded the planetarycone-hemisphere assemblies onto each of the planetary carriers 11, thetwo planetary carriers 11 with their bearings may be positioned on eachside of the main shaft 1. The torque tubes 17 may be aligned with theirrespective hemispheres and the two planetary carriers 11 bolted togetherwith the rods 12. Two diametrically opposite rods 12 may be threadedthrough the rotor carrier driver 2. It is exactly the same for theexpandable planet carrier of FIG. 2a except the halves are not boltedtogether.

FIG. 6 shows an end view of the transmission mechanism according to anembodiment of the present disclosure. In the embodiment of FIG. 6, thereare an equal number of torque tubes 17 and rows of spherical planets 19.In this embodiment there are no planetary shafts, spool bearings orrings around the spool bearings. Referring to FIG. 6, and starting atthe centre, the transmission mechanism includes the main shaft 1, therotor 34, the half-drums 3, the vee-rings 6, the spherical planets 19,and the torque tubes 17. FIG. 6 also shows that the spherical planets 19are barely occluded, perhaps by as little as one fifth their diameter.

FIG. 7 shows how all the outer components may be configured and encased,according to an embodiment of the present disclosure. Two end plates 24and thru-fasteners 16 may all be tightly attached together via nuts 15.Such configuration may result in a very rigid structure. A control ring46 may be disposed at the centre with the reaction rings 25 on eitherside. The control ring 46 may be mounted on the thru-fasteners 16 viaspool-type bearings 45. Links 47 on each side of the control ring 46connect the reaction rings 25 to the control rings 46. Turning thecontrol ring 46 in either direction brings the reaction rings 25 closertogether or further apart in unison, thereby varying the gear ratio. Thecontrol ring 46 may be operated by cable or a small part of its outercircumference may have spur gearing driven by a stepper motor. Thethru-fasteners 16 may not be of circular section but may be concaveshaped (diagonally opposite) to match the curvature of ball bearings 20(illustrated in FIG. 8) as illustrated at the bottom of FIG. 7. Thecontrol ring 46 cannot move longitudinally because of the spool-typebearings 45. FIG. 7 shows the stepper motor 40 and a small part of thecircumference of the control ring 46 which function as spur gearing. Thestepper motor 40 is configured to operate the control ring 46. A nut 39may be used to fix the stepper motor 40 to one of the thru-fasteners 16.FIG. 7 also illustrates a thru-fastener retaining pin 44.

FIG. 8 illustrates two views of a reaction ring 25 according to anembodiment of the present disclosure. The reaction ring 25 may have aplurality of bearing mounts 30. Referring to FIG. 8, the reaction ring25 according to the present embodiment has six double ball bearingmounts 30. Ball bearings 20 may be configured to rotate in the doubleball bearing mounts 30 with very little friction. As illustrated in FIG.7, the section of the thru-fastener 16 may be configured to exactly fitthe space between the spherical planets 19. The links 47 may be boltedonto threaded stubs 42 on either side of the control ring 46 via linkbearings 48. Stub nuts 29 may be used to connect the links 47 to thecontrol ring 46 and the reaction rings 25.

FIG. 9 illustrates a multi-component view of an infinitely variabletransmission system according to an embodiment of the presentdisclosure. FIG. 9 illustrates how the spherical gears 19 are positionedbetween the torque tubes 17. Referring to FIG. 9, the infinitelyvariable transmission system according to the present embodiment maycomprise sixteen planetary cone shafts 26, eight torque tubes 17, andsixteen planetary cone-hemisphere structures 22. Altogether, theinfinitely variable transmission system according to the presentembodiment may comprise eighty spherical planets 19. As each sphericalplanet 19 has two points of contact this embodiment has no less than onehundred and sixty points of contact on the vee-rings 6. As the vee-rings6 constitute part of the output, this is the final drive. These pointsof contact may be highly pressurized and the frictional grip or adhesionon the vee-rings 6 can handle as much torque as a toothed gear wheel.The large number of contact points ensures a wide distribution of theload. A brush gear may be contained in a small housing attached to theoutside of the casing. The other components are described in detail inprevious drawings. FIG. 9 illustrates a main shaft bearing 10 in thecasing.

FIG. 10 shows as many of the components as possible without obscuringother components. Referring to FIG. 10, splines 21 may be provided forsplining the pressuriser rings 4 to the main shaft 1. Also illustratedin FIG. 10 is a carrier mount bearing 23, threads 28 for the pressuriserring 4, and planet carrier assembly nuts 41.

The present disclosure features geared zero and crucial to accomplishingthis in the four-element gear train are two reduction stages in the geartrain. The first is in the joint between the planetary cones 22 andtorque tubes 17 which is approximately 1:0.85. In other words 1 rev ofthe planetary cones 22 only gives 0.85 rev of the torque tubes 17. Thesecond is between the spherical planets 19 and vee-rings 6 where thereduction is approx. 1:0.7. In effect they behave like compound gearwheels. The overall effect is that when the reaction rings 25 engage theplanetary cones 22 at their maximum diameter, the output which is themain shaft 1 is stationary.

Initially, the main shaft 1, which is the output, is stationary, whilethe rotor 34 may be rotating at several thousand RPM. As the reactionrings 25 move along the planetary cones 22, the overall gear ratiochanges from zero output to a gear ratio of approximately 1-3. Thisrequires no final drive as such. The rotor 34 does not drive the mainshaft 1 directly but indirectly through the infinitely variabletransmission system.

In normal operation, the spherical gears 19 drive the vee-rings 6 andthe vee-rings 6 being splined to the half-drums 3 drive the half-drums3. At the same time, the end rings 7 engage with the pressuriser rings 4which in turn drive the main shaft 1. In addition, the load the mainshaft 1 encounters causes the pressuriser rings 4 to compress the endrings 7 inwards, thus forcing the spherical planets 19 radiallyoutwards.

The electrically driven planetary cone transmission assembly of thepresent disclosure has several advantages over designs where input poweris from another source. As the motor ‘stator’ is not fixed, use is madeof the backward torque of the stator to compress the vee-rings andaugment the forces driving the planet assemblies outwards. Manyplanetary designs can go from forward to reverse in one movement of thereaction rings. However, being electrically driven, one can simplyreverse the rotation of the motor for reverse motion. This savesvaluable ratio range. In this design, geared zero or neutral is when thereaction ring is at the larger diameter of the planetary cone. Theassembly is basically an electric motor completely enveloped by thetransmission. The stator differs from a typical motor stator in that itis precision made and balanced.

The purpose of any machine such as this is to drive a load, and via thepressuriser mechanism the load further compresses the vee-rings. Theassembly uses three different forces to force the twin planet coneassemblies out onto the reaction rings. The three forces are:

-   -   1. backward stator torque of the electric motor    -   2. load torque    -   3. centrifugal force

This class of transmission is not only continuously variable butinfinitely variable as well, i.e. it gives neutral or geared zero.Continuously variable transmissions can be adapted to become infinitelyvariable but they require an extra gear set.

Referring now to FIGS. 11A-D, 12, 12A and 13-19, there is providedalternative advantageous embodiments of the transmission system.

FIG. 11A-D illustrate a schematic which is identical with FIG. 1 exceptthe curved end of the hemisphere faces inwards to take account of thedifferent contact circles. In some embodiments, the planetary carriermay be divided in half. Optionally, a pressure plate 43, or pressureplates 43 as shown in FIGS. 11D and 11C respectively, can be insertedbetween each half planet carrier and the bearings 50 at the base of thecones 22 as shown in FIG. 15. The circumference of the plates can haveopen ended slots so that the planet shafts 26 can slide in them. Thecurved portion of the hemisphere may face inwards towards the centre ofthe torque tube, and there are no internal blocking rings. The pressureplates force the cones inwards into the torque tubes providing greatfrictional adhesion between the hemispheres and the torque tubesinternally and the cones and torque tubes externally. The dimensions maybe chosen so that their circles of contact are the same diameter. Thecones will only move out radially if they are held longitudinallystationary and the planet carrier halves diverge from each other. Here,the right half planet carrier is held longitudinally stationary by beingmounted on a bearing in the right casing and the left half planetcarrier pulled left by magnetic forces. The cones are fixedly located inthe torque tubes by the pressure plates.

FIG. 12 provides a view of 6 planet shafts on each half planet carrier11, and it is of the expandable type. It differs from the foregoingembodiments in that the right half carrier has a tubular extension bywhich it is mounted on the right half casing by a ball thrust bearing 10visible in FIG. 19. The left half planet carrier 11 now has the magnetsof an axial flux motor to it. The other change is that the rodsconnecting the halves serve as mounts for the tubular idler planets asshown in FIG. 12A, see also FIG. 18.

The system may additionally comprise a plurality of idler planets. Inthe exemplary embodiment, the idler planets are equal in number to thenumber of torque tubes. By way of example only, six torque tubes and sixidler planets may be provided. These idler planets are tubular and theonly difference between them and the torque tubes is that they are halfthe diameter or less. The idler planets are conveniently mounted on therods 12 connecting the planet carrier halves together. They aretherefore at a fixed radial distance from the central axis. Theycontribute to the spacing of the torque tubes and they facilitategetting a geared zero ratio.

FIGS. 13 and 14 show the same aspects of the rings as FIGS. 3 and 4except that the rotor in FIG. 4 is gone and in FIGS. 3 and 4 the twofour-armed spiders are replaced by one 3-armed spider which is integralwith the main shaft.

FIG. 15 shows the pressure plates 43. Unlike in FIGS. 5 and 5A, thehemispheres have the curves now facing inwards and there are no ringsinside the torque tubes. In the exemplary embodiment, the imaginarycontact circles 35 are of equal diameter.

FIG. 16 uses 6 torque tubes instead of the 8 in the embodiment of FIGS.1-10. The only other difference between it and the embodiment of FIGS.1-10 is that it has the idler planets between the ball gears.

FIG. 17 differs from FIG. 7 in that it shows the axial flux stator 37which is attached to the left end plate. It also shows bearing 36 whichwas omitted in the right casing in the embodiment of FIGS. 1-10.

FIG. 18, similar to FIG. 9, shows as many components as possible withoutobscuring others. It shows all the aforementioned including the idlerplanets 31 and pressure plates 43. As can be seen in FIG. 18, theelectric motor may be positioned at the extreme end of the unit.Advantageously, the motor may be an axial flux motor. The stator of themotor can be conveniently located in the casing of the transmissionsystem avoiding the use of slip rings and the extra wiring involved in acentrally mounted motor. FIG. 18 also shows minor new components 51; 52;53; 54.

The magnets of the rotor can be bonded to the planet carrier: inreality, the basic structure of the motor is already there. Having justone drum instead of two half drums greatly simplifies the structure andthe motor itself will be more straightforward. However great theseadvantages are, it is the powerful attractive force between the rotorand the stator that is the key to unlocking the full potential of thistype of transmission. This force can be exploited to a great extentusing the design of the present disclosure.

With specific reference to FIG. 19, the stator 37 located in the leftcasing 24 attracts the half planet carrier 11 leftwards, the inner raceof its mounting bearing 23 bears against sleeve 51 pushing it leftwardsagainst nut 2 which pulls the main shaft leftwards. Because the arms 13of the spider are integral with the main shaft, they via rollers 5compress the stack of vee-rings leftwards. The cylindrical drum 3 onwhich the vee rings are mounted also moves leftwards. This in turncauses pressure plate 43 to move left. FIG. 15 shows how this pressureplate 43 compresses the cones and torque tube up against thelongitudinally stationary pressure plate 43 on the left. At the sametime as these components are being compressed left, the ball gears arebeing forced out radially which in turn leads to the cones being forcedout against the reaction rings.

In order for power to be transmitted by friction, there must be adhesionbetween: —

1. The reaction ring and the cones2. The cone hemisphere and the torque tube3. The torque tube and the ball gears4. The ball gears and the vee rings

The inventor claims that by means of the mechanisms outlined above, theforce between the stator and rotor will enforce adhesion between allfour of the above interfaces.

This adhesion will be augmented by the load pressurising mechanism.

FIGS. 20A to 29 show an alternative embodiment in which there are noidler planets, and the two pressuriser rings 4 are replaced by a singlepressuriser plate 43 which is different in form and function to thatillustrated in the previous Figures. Nuts 14 in FIG. 11A and components51; 52; 53; 54 in FIG. 18 are also removed.

FIG. 20A shows the main shaft 1 and the thrust bearing 31 which isbetween the spider arms 13 and the rotor tube 21.

FIG. 20B shows the splined tube to mount ball race discs. It consists ofthree components welded together, a tube 3, the end ball race disc 7,and the cam inclines 49 previously called drum. The splined tube maypreferably have a uniform diameter in some embodiments, and inalternative embodiments a variable diameter as desired.

FIG. 20C is the same as FIG. 11C but without the two pressurizer plates43.

FIG. 20D shows the new pressurizer plate 43 which replaces the twopressurizer rings 4, and which comprises three cutaways to accommodatethe narrow ends of the cones. FIG. 20D also shows thrust bearing 9 whichis between the new pressurizer plate 43 and the end ball race disc 8.

FIG. 21 shows how two half planet carriers are combined together in adifferent way to the preceding embodiments. Each half can have severalprojecting planet shafts to hold the cone/hemispheres. The drawing inFIG. 21 shows just three as this is judged to be the optimum number,although other numbers may be feasible in various embodiments. The lefthalf has three long fixedly attached rods which slide throughcorresponding holes in the other half to be bolted to the rotor of theelectric motor. In certain embodiments of the present disclosure ach ofthe planet shafts comprises an inner element and outer element. Theinner element may comprise a section, such as rectangular section 11visible in FIG. 21, bonded to its respective planetary carrier. Theouter element may comprise a tube with an inner rectangular section suchthat it slides freely on the inner element. Preferably, the outerelement is also configured to be capable of sliding slightly outwardsradially.

FIG. 22 shows the rotor of the axial flux motor. It consists of a discmounted on a tube. Magnets 34 are bonded to one side of the disc. Suchmotors normally have a thrust bearing to prevent the rotor hitting thestator with catastrophic results. This unit has one for the same reasonsbut it is not used to counter the great force between the rotor and thestator. That force is used to pressurise the components and although thebearing is not necessary it is retained case of failure in adjustment,etc.

FIG. 23 is a perspective of ten ball race discs located around the mainshaft and splined tube. It also shows some of the ball gears 19 inposition.

FIG. 24 shows a drawing with the same ten ball race discs and theirassociated ball gears 19. For the first time it shows the newlyintroduced ball gear retaining rings 28.

FIG. 25 is the same as FIG. 15 but without the two pressurizing rings43.

FIG. 26 shows a cross section of the transmission according to theembodiment of FIGS. 20A-29. The idler planets are removed, enabling eachplanetary ring assembly to be independent of its neighbour. This is bymerit of the newly introduced ball gear retaining rings 28. An importantpoint to note in FIG. 26 is that the torque tube can be close to theball race disc and the ball gear retaining ring, but they must nottouch. The ball gear retaining rings 28 perform the same function as theidler planets which they replace. They stop the ball gears 19 fromflying radially outwards but they have two advantages over the idlerplanets. In one regard, they allow the full radial force outwards to beapplied to the reaction rings whereas the idler planets absorb aconsiderable amount. In another regard, each planetary cone assembly isindependent of its neighbour so that as few as three assemblies can beused which has its own advantages. Under outward radial pressure, theball gears automatically space themselves diametrically opposite to eachother in their respective retaining rings thereby dispensing withbearing cages. For this to happen the components involved, namely thetorque tube, ball gear and ball race disc are preferably dimensionedsuch that the torque tubes do not touch the rings 28 nor the ball racedisc 6.

FIG. 27 is the same as FIG. 17 except that the stator of the electricmotor is in the right casing.

FIG. 28 shows the motor stator in the right casing and the default 14.Preferably, the electric motor is positioned on the same side as theload thrust mechanism, namely the spider arms 13. When the motor is onthe same side as the mechanism generating the load force, the spider onthe main shaft 1 rolling on the cam inclines of FIG. 20B, their twoforces augment each other.

FIG. 29 shows as many components as possible without obscuring others.It shows the direction of the compressing forces. It shows the defaultbearing 14 (as does FIG. 28) in the default position. In normaloperation, the stator which is located in the right casing is screwedwith nuts 15 further away from the rotor taking the pressure off thedefault bearing and putting it on the components. The usual distance isjust a few millimetres.

The words comprises/comprising when used in this specification are tospecify the presence of stated features, integers, steps or componentsbut does not preclude the presence or addition of one or more otherfeatures, integers, steps, components or groups thereof.

1. An infinitely variable multi-epicyclic friction transmission systemfor an electric motor comprising: a casing for the infinitely variablemulti-epicyclic friction transmission system; a main shaft and aplurality of ball race discs located around the main shaft; a splinedtube comprising a tube, an end ball race disc of the plurality of ballrace discs, and a plurality of cam inclines, wherein the splined tube isconfigured to bear the plurality of ball race discs, and splined on anouter circumferential surface so that the plurality of ball race discscan slide longitudinally along the splined tube; an axial flux motorcomprising a stator which is fixedly located in a side plate of thecasing for the infinitely variable multi-epicyclic friction transmissionsystem; a default thrust bearing mounted on the main shaft between arotor and the stator to prevent physical contact therebetween; aplurality of twin planetary cone assemblies attached to at least oneplanetary carrier and disposed circumferentially around the splinedtube, wherein each twin planetary cone assembly comprises a torque tubeand a planetary cone-hemisphere structure provided at each end of thetorque tube, wherein each planetary cone-hemisphere structure comprisesa planetary cone integral with a hemisphere at its apex such that theplurality of twin planetary cone assemblies comprise hemispheres andtorque tubes, wherein each planetary cone-hemisphere structure isconfigured to roll inside a respective torque tube via a respectivehemisphere, and wherein a slant height of each planetary cone isparallel to the main shaft; a series of spherical planets configured toalternate with the plurality of ball race discs; a pressurizer platecomprising three cutaway portions suitable to accommodate narrow ends ofeach of the plurality of twin planetary cone assemblies; at least onereaction ring disposed around each of the plurality of twin planetarycone assemblies and configured to slide along the planetary cone of eachtwin planetary cone assembly of the plurality of twin planetary coneassemblies to vary a gear ratio; and a plurality of ball gear retainingrings, wherein each of the plurality of ball gear retaining rings ismounted on one of a plurality of ball gears which are mounted on theplurality of ball race discs.
 2. The infinitely variable multi-epicyclicfriction transmission system of claim 1, wherein the planetary cone andthe torque tube are dimensioned such that their circles of contact are asame diameter on the torque tube and the hemispheres.
 3. The infinitelyvariable multi-epicyclic friction transmission system of claim 1,wherein the electric motor is located at an extreme end of theinfinitely variable multi-epicyclic friction transmission system.
 4. Theinfinitely variable multi-epicyclic friction transmission system ofclaim 1, wherein the electric motor is positioned on a same end of theinfinitely variable multi-epicyclic friction transmission system as aload thrust mechanism.
 5. The infinitely variable multi-epicyclicfriction transmission system of claim 1, wherein the plurality of caminclines on one side of the plurality of ball race discs are configuredto be engaged with a load thrust mechanism on the main shaft, whereinthe load thrust mechanism comprises a three-armed spider.
 6. Theinfinitely variable multi-epicyclic friction transmission system ofclaim 1, wherein the plurality of ball gears associated with theplurality of ball race discs are further operable to function as ballbearings in the infinitely variable multi-epicyclic frictiontransmission system.
 7. The infinitely variable multi-epicyclic frictiontransmission system of claim 1, wherein the plurality of ball race discsare configured to be compressed together from a distal end of thesplined tube towards a motor end of the splined tube thus forcing thespherical planets radially outwards.
 8. The infinitely variablemulti-epicyclic friction transmission system of claim 1, wherein therotor comprises a disc with magnets, in a halbach array or otherwise,bonded onto the outer circumferential surface facing the stator andmounted on the main shaft.
 9. The infinitely variable multi-epicyclicfriction transmission system of claim 1, wherein each planetary coneassembly is configured to move out radially away from the main shaft.10. The infinitely variable multi-epicyclic friction transmission systemof claim 1, wherein the plurality of twin planetary cone assemblies aremounted in the at least one planetary carrier.
 11. The infinitelyvariable multi-epicyclic friction transmission system of claim 1,wherein the at least one planetary carrier comprises two planetarycarriers coupled to each other and mounted on the main shaft.
 12. Theinfinitely variable multi-epicyclic friction transmission system ofclaim 1, comprising between three and six twin planetary coneassemblies.